Hydraulic transmission apparatus.



E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS. APPLIoATIoN Hmm 11110.15. 1911.

1,106,245, Patented' Aug. 4, 1914.

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E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS.

APPLICATION FILED DEO. l5, 1911.

Patented Aug. 4, 1914,

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E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS.

APPLICATION FILED DECLlB, 1911.

Patented Aug. 4, 1914.

BSHEETB-SHBET 3.

ffl 2 E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS. APPLICATION FILED DEO.15, 1911.

1,1 06,245.,` Patented Al1g.41 1914.

8 8HEETS-SHEET 4.

E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS.

APPLICATION FILED DBO.15. 1911.

Patented Aug. 4, 1914A a sHBnTssnsnT 5. l

E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS. APPLIUATION FILED 11110.15. 1911.

8 SHEETS-SHEET 6.

E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS. APBLIUATION FILED 1320.15, 1911.

1,106,245. I Patented Aug. 4, 1914.

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E. SCHNEIDER. HYDRAULIC TRANSMISSION APPARATUS. APPLIoAjrIoN FILED 1130.15. 1911.

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ratus for the transmission of movement 1n srarns P HYDRAULIC TRANSMISSION APPARATUS.

To all whom 'it may concern:

Be it known that I, EUGNE SCHNEIDER, a citizen of the Republic of France, residing at Le Creuzot, Sane-et-Loire, France, have invented new and useful Improvements in Hydraulic Transmission Apparatus, which is fully set forth in the followingspecification.

The present invention has for its object improvements in the known hydraulic appawhich a driving pump actuated by a motor and a driven pump are combined with a distributing mechanism interposed between them, the changes of speed and of direction of running of the driven shaft being obtained by means for varying the eccentricity of the cylinders ofthe driving pump relatively to the motor. These improvements are applicable to apparatus of the type :in which the cylinders of the pumps are carried radially on a drum, the pistons bearing by means of a connecting member such as a rod. upon the eccentric device proper, which is then constituted bya shaft parallel with the driving shaft and which is adapted to be separated from or brought closer to the geometrical extension of the axis of the driving shaft at will from the exterior. In these known devices the relative movements between the cylinders and the pistons necessarily give rise to'lateral thrusts by reasonV of the oblique thrust which, as regards the greater number of cylinders, each connecting member (rod or the like) exerts, at reach moment, upon the corresponding piston. In accordance with the invention these lateral thrusts which produce ovalization of 4the cylinders and pistons-are avoided. Between each piston and the thrust member which bears upon the eccentric device proper, an auxiliary thrust member is interposed. The radial movements of this auxiliary member are entirely integral with those of the piston while relatively to the latter they preserve a certain liberty of lateral movement. This interposed auxiliary thrust member is perfectly guided by means of lateralprojectio-ns in radial guides carried by the drum carrying the cylinders.

Figures 1 to 7 of the accompanying draw- `ing1 represent one embodiment of an apparatus provided with the improvement set forth above. Fig. 1 is a longitudinal axial section of the two pumps. Fig. 2 is a cross section to a larger scale on the median plane l Specification. of I-.etters Patent.`

. Application led December 15, 1911.

Patented Aug. 4, 1914i.

Serial No. 666,055.

A A of one or other of the two pumps. Fig. 3 is a cross sectionon the line B-B of the separator plate. Fig. 4 is a cross section on the line C C of the driving pump. Fig. 5 shows the faces of the drums. Fig. 6 represents the faces of the separator plate. Fig. 7 is a horizontal section on the axis of the two pumps on the line E--E in Fig. l. Figs. 8, 9 and l0 show respectively in longitudinal section, in vertical cross section on the line A--A in Fig. 8 and in, partial horizontal section, a modification of the auxiliary thrust device of the pistons, eliminating lateral strains between the latter and the cylinders.

The driving pump which is represented mainly in the left lzand part of Fig. 1 and in Fig. 2 .is constituted by a drum or barrel 1 which 1s driven by the shaft a. rotating in a fixed casing 2 assembled with the separator plate 8. Upon its periphery this drum carries a certain number of cylinders (seven for example) arranged along equidistant radii. Each of these cylinders, which are marked 4, i, It, 4, 4, 4f, 4g, is provided with a conduit 5 ending on the circular face of the drum l which is in contact with the separator plate 3. Within each ot the said cylinders is a piston which in the driving pump is reciprocated as the drum l and cylinders revolve by means of disks l2 mounted on an adjustable trunnion 20. For this purpose and to insure a perfect radial movement of each piston in its cylinder and to avoid all lateral thrust each piston is pro,- vided interior-1y. with a spherical socket or housing :tor receiving one end of a dumbbell shaped rod 7. the opposite head of the rod 7 being received in a spherical housing in a'member 8 provided exterior-ly .with oppositely disposed trunnions'f) on which are mounted anti-friction rolls 10 and 11, rolls l() being adapted to run on disks 12 and the rolls 11 being guided by radial slide ways 13 integral with the drum l. .The parts of this ball and socket connection are held together by a sleeve S. The common axis of trunnions 5l should preferably pass through the center of the head of the rod 7 which is housed in member 8. Each of the rollers 10 is arranged opposite a disk 12 which in Figs. 1 and 2'is represented as being eccentrically located in the upward direction relatively to the axis of the drum l (its position can however vary as will hereinafter be explained). The rollers 11 engage with radial slide ways 13 :forming one with the drum 1.

'llhe driven pump which is represented in the right hand part oit Fig. v1, is composed of elements similar "to those of the driving pump with the sole dier'encethat the two disks 12 occupy an invariable position of eccentricity relatively to the axis of rotation of the drum 1. On the left, hand side of Fig. l, the separator plate 3 presents acircular slide face 14 to which the slide face 15 of the drum 1 is applied. The face 15pre sents seven orifices 16 (Fig. 5) forming continuations of the conduits 5 of the cylinders 4 and theface 14 presents two symmetrical orifices 17 and 18, elongated in form andY continued at their extremities by points; these two orifices 17 and 18 pass right through the separator plate 3 (Fig. 7 ).l

Considering first Fig. 2 as representing the driving pump (left handpump Fig. 1) and assuming the drivingshat'tto rotate in the direction indicated by the arro`w37 carrying with it the drum 1, the cylinders 4, the forks 8 and the rollers 10 andll, it will be noted that the rollers 10", 10, 10d corresponding with the cylinders 4", 4c, 41 are pressed outward by the two eccentric disks '12; by the intermediary of the members 8 and of the rods A7 these rollers cause the corresponding pistons 6 to enter their cylinders and consequently to force liquid through the con'- duits 5 and the orifices 16 into the orifice 17 of the separator plate. The pistons remain .ering Fig. 2 as representing the driven pump perfectly centered'in their cylinders as lateral thrusts can onlyv occur between the rollers 11 and the slide-ways 13; Now considit will be noted that in the position shown'it is the three cylinders4", 4, 4d that are in communication vwith the orifice' 17 of the separator plate; the 'liquid under pressure which enters through this o'riice 17 there- Afore tends to litorce back the pistons ofthe said three cylinders and these pistons press their rollers 1() against the disks'12. Now it will be noted that owing to the eccentricity of these two ldisks the direction of these thrust eHorts does not pass through the center of the disks; consequently at the point ont contact oeach o-theserollers with the corresponding disk a tangential component .is produced; as, on the other hand, the friction resulting from the thrust of the rollers upon the disks 12 is almost nz'l owing to the 'fact that the said rollers are mounted on balls, it follows that thesaid tangential component is, in practice', entirely utilized for producing a movement of rotation of the drum l in the direction indicated by the arrow 38. Itwill also be noted that the rotation of the drum is Inot produced bythe pist-ons bearing laterally against the cylinders, but by the tangential pressure ot the rollers 11 which are mounted on the same 'maximum speed-and oppositely to the drivtrunnions 9 `as the rollers 10 and which run in the slideways 13 integralk with the drum 1;'the-rollers 11 can also be mounted on balls as shown in the drawing. Consequently, the tangential pressure that they produce in running on the slideways 13 does not give rise to any appreciable friction. Finally, as the drum 1 is carried at its two extremities upon rings of balls, it follows that the whole of the tangential components of the rollers 10", v10, 10d4 is utilized with the maximum etti;

ciencvy for producing the rotation of the l drum l of the driven pump because the only real friction that has` to be considere] during the said rotation is that produced between the two faces 14 and 15.

1t will readily be seen that in the position illustrated in Fig. 2 while the cylinders 4", 4, 41 of the driving pump send liquid under pressure through the orifice 17 to 'thecylinders 4b, 4, 4d of the driven pump, inversely by thfe fact of the rotation impartedto the` driven pum the cylinders 4e, 4f, 4g of the latter send lback the liquid that they con,

Vtained to the cylinders 4e 4f 4g of the driving pump through the orifice 18. The same liquid therefore circulates indefinitely bev tween the two pumps, passing under pressure from the driving pump to the driven pump throughthe orifice 17 and returning from the driven pump to the driving pump through the. orice 18 under the influence of the slight counter pressure produced by the pistons" of the driven pump, which7 after havingproduced their driving eifort upon the two disks 12 in passing through a seam circumference, are forced back into their respective cylinders in passing through the other half circumference, owing to the eccentricity of these disks. rllhis pistons 4*?, 4f, 41g of the driving pump should therefore be held in contact with the' disks '12 by the said counter pressure but by way of precaution a ring 19 has been provided for each group of rollers 10; this ring surrounds them in such a manner as to hold them constantly in Contact with the disk' 12. Whilethe' two disks 12 of the driven-pump always present i the same veccentricity relatively to` theA axis of rotationof the durm 1, the eccentricity of the disks 12 Aof the driving pumpis ad justable; they are mounted on the trunnionI 20 which is integral withan anehor 21 ar- 1,106,245 l j i 3 ing pump. If the anchor be caused to descend progressively the eccentricity of the disks 12 of the driving pump is diminished; the delivery from the latter diminishes and the driven pump rotates less vand less rapidly. When the descent of the anchor brings the center of the double disk 12 into coincidence with the axis of rotation of the drum 1, the delivery from the driving pump becomes zero and the driven pump stops. In continuing to lower the anchor the disks 12 are rendered eccentric in the downward di rection; it is then the cylinders of the driving pump Which pass to the right of Fig. 2

which deliver through the orifice 18 liquid under pressure to th'e drivenA pump; the di rection of rotation of the latter is then changed, that is to say it rotates in the same direction as the driving pump and through the orifice 17 delivers to the latter the liquid which issues from its cylinders. )Vith the object of avoiding hydraulic re` coils, which might arise from an abnormal resistance Aupon the driven shaft or from any other cause, each of the orifices 17 and 18 of'the separator plate comprises: 1. A delivery valve 24 (Fig. 3) intended to enable the liquid under excess pressure at a given moment to escape into the reservoir. 2. A suction valve 25 (Fig. 3) owing to which any vacuum produced in the pumps would immediately ,be compensated for vby an admission of liquiddrawn from the reservoir. (These latter valves also serve for automatically filling the pumps on first starting).

` In the example illustrated in Figs. 8, 9 and 10 each of the members 8 bears by means of a head b of spherical convexity against a corresponding Spherical concavity a of the piston. Upon a shaft-0, carried by the head b, a roller 10 is mounted inside this head. The member 8 is provided externally, as in the preceding example, with two trunnions 9 the geometrical axis of which coincides preferably with that of the shaft c and upon each of which there is mounted a roller 11. The rollers 11 are in engagement in the radial slideways 13 integral with the drum 1.

In the embodiments of the invention described abuve, each of the drumsl is carried by ball bearings; one ofv them l(26 Fig. 1) is established between the end cup of the cas y ing 2 and the shaft which is itself integral `with the drum 1 by means of a central nip lple 27 and teeth 28. The other bearing 29 is established between the d rum 1 and the separator plate 3. On the other hand a spring' 3() interposed between the plug 37 of ,the casing 2 and a ball bearing 31, presses the drum longitudinally so as to apply it exactly against the slide face 14. Or an automatic thrust device for the slide faces might be employed. For each of the pumps this device comprises a cylinder 32 provided with a` cupped leather which permits of causing the liquid under pressure to act upon a certain annular section ofthe shaft; this liquid under pressure enters the conduit 38 through one or other of the valves or 34 (Fig. 3), which rises under the influence of the pressure which exists, yaccording to the direction sof rotation in one or other of the conduits 17 or 18.

The apparatus is provided with a reservoir 35 (Fig. 1) serving on the one hand to compensate for losses of oil by supplying the same through passages 35, Fig. 1, and 35", Fig. 3, to the interior of the apparatus and on the other hand to permit of the expansion of the oil resulting-from the heating due to prolonged operation. For this purpose 4passages 24a are provided in the separator plate 3 between the exterior space of the drums 1 and the Valve controlled spaces 17 and 18. Slee Figs. 3 and- 7. Two tubular sockets 36 pass through this reservoir and serve for filling and for the escape of the air from the casings 2.

In the embodiments of the invention which have just been described, a spherical joint is provided between each end plate 1, Fig.` 1, of the cylinder carrying drums 1 and the corresponding bearing face 14l of plate 14 which 'is fast to the separator plate 3. The center of each spherical joint is located at the intersection of the longitudinal axis of the apparatus and a median vertical plane of each outer bearing. In Fig. 1 only one center m is thus indicated. This arrange ment presents the advantage of enabling the drum to adjust itself always on the distributer notwithstanding slight imperfections of construction or fitting and this is impossible with plane slide faces in which the least in-l exactitude in the construction or finish makes itself felt in defective perpendicularity of the slide face of the drum upon the actual axis of rotation determined by the centers of the supporting bearings 26, 29 of the drum upon the casing; from this it follows that the drum and the distributer no longer present the absolute contact necessary for a perfect joint.

Although spherical slide faces present the advantage indicated above as compared with plane faces, it is Vstill necessary in order to insure a good joint, to have recourse to a certain pressure of application which gives rise to loss of work due to friction.

WhatI claim as my invention and desire Ato secure yby Letters Patent in the United States is Y l. IIn a hydraulic transmission apparatus 0f the character described, the combinationof a plurality of radially disposed revolubly mounted cylinders, pistons working in said cylinders and thrust members having jointed connections with the pistons and provided with lateral projections, guides engaging llo D said projections arranged parallel Withthe axes or the cylinders whereby lateral thrust of the' pistons on the cylinders is avoided and means for reciprocating said Athrust members. l

2. in a hydraulic transmission apparatus of the character described,the combination` of the character described, the combination of a plurality of radially disposed revolubly m'ounted cylinders, pistons Working in said cylinders, an adjustable cam for regulating the throiv of the pistons, thrust members having jointed connections With said pistons land provided With anti-friction bearings traveling on said cam and means for guiding each thrustme'mloerA in line with the axis ot' its cylinder.

4. ln a hydraulictransmission apparatus of the character described, the combination of a plurality of radially disposed revolubly mounted cylinders,pistons Working in said cylinders,cam disks adjustably mounted and adapted to regulate the throw of said pis'- tons, thrust members having jointed connections With said pistons and provided with anti-,friction bearings traveling on said cam disks, means retaining said bearings on said,A disks as the cylinders revolve, and means guiding cachot said thrust members in line with the aXesot said cylinders.V

5. ln'a hydraulic transmission apparatus of the character described,the combination of a rotary cylinder motor and a rotary cylinder pump, a separator plate having openings through which said motor and pump may communicate, and means intermediate tering the latter.

6. in a hydraulic transmission apparatus said plate and each of said elements for ceny of the character described, the combination of a pump having a rotary casing, a motor having a rotary caslng, and a separator plate ,intermediate said elements and having openings throughwhich said pump and motorY may communicate and presenting concave surfaces, said -casings having corresponding I R. nn SEvELINGes. 

